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WO1994002757A1 - Friction-damped tensioner for belt or chain drives - Google Patents

Friction-damped tensioner for belt or chain drives Download PDF

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Publication number
WO1994002757A1
WO1994002757A1 PCT/EP1993/001809 EP9301809W WO9402757A1 WO 1994002757 A1 WO1994002757 A1 WO 1994002757A1 EP 9301809 W EP9301809 W EP 9301809W WO 9402757 A1 WO9402757 A1 WO 9402757A1
Authority
WO
WIPO (PCT)
Prior art keywords
friction
tensioning
damped
base part
clamping system
Prior art date
Application number
PCT/EP1993/001809
Other languages
German (de)
French (fr)
Inventor
Hellmut Adler
Rudolf Polster
Michael Schmid
Original Assignee
Ina Wälzlager Schaeffler Kg
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Ina Wälzlager Schaeffler Kg filed Critical Ina Wälzlager Schaeffler Kg
Priority to JP50411194A priority Critical patent/JP3194954B2/en
Priority to US08/356,329 priority patent/US5458541A/en
Priority to KR1019950700319A priority patent/KR100260962B1/en
Publication of WO1994002757A1 publication Critical patent/WO1994002757A1/en

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H7/00—Gearings for conveying rotary motion by endless flexible members
    • F16H7/08—Means for varying tension of belts, ropes, or chains
    • F16H7/10—Means for varying tension of belts, ropes, or chains by adjusting the axis of a pulley
    • F16H7/12—Means for varying tension of belts, ropes, or chains by adjusting the axis of a pulley of an idle pulley
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B67/00—Engines characterised by the arrangement of auxiliary apparatus not being otherwise provided for, e.g. the apparatus having different functions; Driving auxiliary apparatus from engines, not otherwise provided for
    • F02B67/04—Engines characterised by the arrangement of auxiliary apparatus not being otherwise provided for, e.g. the apparatus having different functions; Driving auxiliary apparatus from engines, not otherwise provided for of mechanically-driven auxiliary apparatus
    • F02B67/06—Engines characterised by the arrangement of auxiliary apparatus not being otherwise provided for, e.g. the apparatus having different functions; Driving auxiliary apparatus from engines, not otherwise provided for of mechanically-driven auxiliary apparatus driven by means of chains, belts, or like endless members
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D69/00—Friction linings; Attachment thereof; Selection of coacting friction substances or surfaces
    • F16D69/02—Composition of linings ; Methods of manufacturing
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H7/00—Gearings for conveying rotary motion by endless flexible members
    • F16H7/08—Means for varying tension of belts, ropes, or chains
    • F16H7/10—Means for varying tension of belts, ropes, or chains by adjusting the axis of a pulley
    • F16H7/12—Means for varying tension of belts, ropes, or chains by adjusting the axis of a pulley of an idle pulley
    • F16H7/1209—Means for varying tension of belts, ropes, or chains by adjusting the axis of a pulley of an idle pulley with vibration damping means
    • F16H7/1218—Means for varying tension of belts, ropes, or chains by adjusting the axis of a pulley of an idle pulley with vibration damping means of the dry friction type
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B2275/00—Other engines, components or details, not provided for in other groups of this subclass
    • F02B2275/06—Endless member is a belt
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B2275/00—Other engines, components or details, not provided for in other groups of this subclass
    • F02B2275/08—Endless member is a chain
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H7/00—Gearings for conveying rotary motion by endless flexible members
    • F16H7/08—Means for varying tension of belts, ropes, or chains
    • F16H2007/0802—Actuators for final output members
    • F16H2007/081—Torsion springs

Definitions

  • the invention relates to a friction-damped tensioning system for belt or chain drives, which is preferably used in internal combustion engines, according to the features of the preamble of claim 1.
  • a housing is provided, on which a tensioning part which can be pivoted on one side is attached to accommodate a tensioning roller.
  • the device is, for. B. attached to the crankcase of an internal combustion engine.
  • the shaft of the screw is surrounded in the housing by a bearing part, on the outer surface of which a torsion spring, embodied as a coil spring, is guided, which is supported at one end on the flange of the bearing part and at the opposite end on the pivotable clamping part.
  • a damping device is inserted between the flange of the bearing part and a carrier plate of the device.
  • the torsion spring causes the tensioning roller to shift in order to maintain a predetermined belt tensioning force by pivoting the tensioning part. This results in a damped actuating movement by the damping device.
  • An elastomer friction disk serves as the damping device, in which the friction coefficient is disadvantageously temperature-dependent.
  • the friction surface In order to achieve a long service life for the friction lining, that is to say avoidance of inadmissible heating and high wear, the friction surface must be enlarged or reduced Spring force necessary. Both measures adversely affect the function or the required space of the device.
  • a friction lining consisting of an organic material.
  • the asbestos-free material which is advantageously used has material properties whose maximum surface pressure reaches 2 N / mm 2 and thereby clearly exceeds the value of 0.5 N / m customary for plastics (eg elastomers or thermoplastics) .
  • the coefficient of friction of the material according to the invention advantageously has temperature-dependent changes that are negligible compared to plastics. Due to the higher permissible surface pressure, a friction lining that can be used with smaller radial dimensions can advantageously be used, which consequently enables the entire clamping device to be designed in a smaller space, which results in a significant cost advantage.
  • the structural design of the tensioning device provides for a division of the spring force of the clamped torsion spring, by means of which a pretensioning force is achieved on the belt or chain in the circumferential direction, and the friction lining used for damping is only subjected to an axial force. Regardless of the position of the clamping part relative to the base part, there is no dependence on the frictional torque according to the invention, since the friction element and thus the friction lining is acted upon by an axial force which remains constant.
  • the friction lining is advantageously also not subjected to any deformation work which has prevented the maintenance of a constant friction coefficient in previous clamping systems and thus reduced the life of the friction lining.
  • a non-asbestos-free friction material based on graphite-duroplastic rubber with a synthetic fiber reinforcement, with which a very high wear resistance can be achieved is used as a suitable material for the friction lining.
  • the friction disk rests frictionally on the friction lining, which is attached to the base part.
  • the friction lining can be fastened to the friction disk and bear frictionally against the base part.
  • the radial dimension and arrangement of the friction lining is advantageously chosen so that it coincides with the force application surface of the spring, the friction lining being separated from the spring by the base of the base part.
  • the idea of the invention can also be transferred to a friction lining design in which the friction lining is neither attached to the friction disk nor to the base part, but is used as a loose part.
  • the friction lining is advantageously designed in the geometrical form of an annular disk. Alternatively, it is also possible to design the friction lining in the form of axially or radially guided circular ring segments.
  • the idea of the invention provides that the outer wall, the outer surface of the base part, covers the friction disk axially and radially and thus also includes the friction lining. At the same time, this design results in a compact design which takes up little radial and axial space.
  • the shaft of the clamping part should be roller-mounted in the base part, with at least one needle collar being used for the roller bearing, the roller bodies of which are located directly between the housing (base part) and the shaft (clamping part). are used, which are each provided with raceways for the rolling elements.
  • the clamping system 1 is illustrated by a sectional view. Thereafter, the clamping system 1 is provided with a base part 2, which has a largely rotationally symmetrical shape and which on a lateral surface 3 with two radially opposite tabs 4 for fastening the clamping system 1 to a housing, not shown, for. B. is provided a crankcase of an internal combustion engine. Centrally, the base part 2 is provided with a sleeve 6, which extends from an end of a base 5 and extends axially over the opposite end of the lateral surface 3. A shaft 7 inserted into the sleeve 6, which is supported by slide bearing bushes 8, establishes a rotary connection between a clamping part 9 and a friction disk 10.
  • the clamping part 9 or the friction disc 10 is rotatably, for. B. connected via a toothing 11 to the corresponding component, the stepped end, provided with the toothing 11, of the shaft 7 being caulked with the clamping part 9 or the friction disk 10 for rotational fixing.
  • a spring 13 is arranged as a torsion spring, which is designed as a helical spring, and in the operating position of the tensioning system 1 the tensioning part 9 is always in a belt or chain tension increasing position pivoted.
  • the spring 13 To fix the spring 13 in rotation, its ends are secured to the base 5 or to the tensioning part 9 by means of retaining plates 19.
  • the clamping part 9 is provided on its end face opposite the base part 2 with a housing extension 14, into which a fitting bore 15 with a subsequent threaded bore 16 is made. These bores 15 and 16 serve to receive and fasten a tensioning roller which is not shown and which is connected to a chain or belt drive.
  • An axial force exerted by the spring 13 on the clamping part 9 is transmitted via the shaft 7 to the friction disk 10, which exerts a force on the friction lining 18 and thus causes an intentional damping of the movement of the clamping part 9, e.g. B. when shock loads occur in the belt or chain drive.
  • the outer surface 3 of the base part 2 is extended axially over the base 5, as a result of which the friction lining 18 is covered axially and radially by the base part 2 and is arranged in an almost completely protected manner by including the friction disk 10.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Devices For Conveying Motion By Means Of Endless Flexible Members (AREA)
  • Braking Arrangements (AREA)

Abstract

The invention relates to a tensioning system for a belt or chain drive. Tensioners are known in which there are plastic friction bushes to damp oscillations where the coefficient of friction is adversely affected by temperature effects. It is the purpose of the invention to provide a tensioning system in which the friction coating retains a virtually constant frictional torque throughout its useful life. To this end, according to the invention there is a basic component (2) in which against a base (5) in the shape of a circular disc bears a friction coating (18) on which is supported a friction disc (10) which is secured against rotation by means of a shaft (7), to the tensioner (9) producing the oscillating movement.

Description

Beschreibung description
Spannsystem, reibungsgedämpft für Riemen- oder KettentriebeTensioning system, friction damped for belt or chain drives
Die Erfindung bezieht sich auf ein reibungsgedämpftes Spannsystem für Riemen- oder Kettentriebe, das bevorzugt in Brennkraftmaschinen einge¬ setzt ist, nach den Merkmalen des Oberbegriffs von Anspruch 1.The invention relates to a friction-damped tensioning system for belt or chain drives, which is preferably used in internal combustion engines, according to the features of the preamble of claim 1.
Eine derartige Vorrichtung ist der DE-A-3225411 zu entnehmen. Danach ist ein Gehäuse vorgesehen, an dem ein einseitig schwenkbares Spann¬ teil zur Aufnahme einer Spannrolle angebracht ist. Mittels einer zentrisch durch das Gehäuse geführten Schraube ist die Vorrichtung z. B. am Kurbelgehäuse einer Brennkraftmaschine befestigt. Der Schaft der Schraube ist im Gehäuse von einem Lagerteil umgeben, auf dessen Man- telfläche eine Torsionsfeder, ausgeführt als Schraubenfeder, geführt ist, die sich an einem Ende am Flansch des Lagerteils und an dem gegenüberliegenden Ende am schwenkbaren Spannteil abstützt. Zwischen dem Flansch des Lagerteils und einer Trägerplatte der Vorrichtung ist eine Dämpfungseinrichtung eingesetzt. Im eingebauten Zustand bewirkt die Torsionsfeder eine Verlagerung der Spannrolle zur Beibehaltung einer vorgegebenen Riemenspannkraft, indem das Spannteil verschwenkt wird. Dabei kommt es zu einer gedämpften Stellbewegung durch die Dämpfungseinrichtung. Als Dämpfungseinrichtung dient eine Elastomer- Reibscheibe, bei der sich der Reibkoeffizient nachteilig tempεratur- abhängig verhält. Zur Erreichung einer hohen Standzeit des Reibbela¬ ges, das heißt Vermeidung einer unzulässigen Erwärmung und eines hohen Verschleißes ist eine Vergrößerung der Reibfläche oder eine reduzierte Federkraft notwendig. Beide Maßnahmen wirken sich auf die Funktion oder auf den erforderlichen Bauraum der Vorrichtung nachteilig aus.Such a device can be found in DE-A-3225411. According to this, a housing is provided, on which a tensioning part which can be pivoted on one side is attached to accommodate a tensioning roller. By means of a screw guided centrally through the housing, the device is, for. B. attached to the crankcase of an internal combustion engine. The shaft of the screw is surrounded in the housing by a bearing part, on the outer surface of which a torsion spring, embodied as a coil spring, is guided, which is supported at one end on the flange of the bearing part and at the opposite end on the pivotable clamping part. A damping device is inserted between the flange of the bearing part and a carrier plate of the device. In the installed state, the torsion spring causes the tensioning roller to shift in order to maintain a predetermined belt tensioning force by pivoting the tensioning part. This results in a damped actuating movement by the damping device. An elastomer friction disk serves as the damping device, in which the friction coefficient is disadvantageously temperature-dependent. In order to achieve a long service life for the friction lining, that is to say avoidance of inadmissible heating and high wear, the friction surface must be enlarged or reduced Spring force necessary. Both measures adversely affect the function or the required space of the device.
Aufgabe der Erfindung ist es daher, eine Spannvorrichtung zu schaffen, die ein nahezu konstantes Reibmoment, unabhängig von der Temperatur über die Lebensdauer des Spannsystems sicherstellt, und die einen geringen Verschleiß aufweist sowie eine relativ geringe Reibfläche benötigt.It is therefore an object of the invention to provide a tensioning device which ensures an almost constant friction torque, regardless of the temperature over the life of the tensioning system, and which has little wear and requires a relatively small friction surface.
Diese Aufgabe wird erfindungsgemäß durch die im Kennzeichen des An¬ spruchs 1 angegebenen Merkmale gelöst.This object is achieved according to the invention by the features specified in the characterizing part of claim 1.
Erfindungsgemäß ist ein aus einem organischen Material bestehender Reibbelag vorgesehen. Das vorteilhaft zur Anwendung kommende asbest- freie Material weist dabei Werkstoffeigenschaften auf, deren maximale Flächenpressung 2 N/mm2 erreicht und dabei deutlich den von Kunst¬ stoffen (z. B. Elastomeren oder Thermoplasten) üblichen Wert von 0,5 N/m übersteigt. Der Reibkoeffizient des erfindungsgemäßen Materials besitzt vorteilhaft gegenüber Kunststoffen vernachlässigbare tempera- turabhängige Änderungen. Bedingt durch die höhere zulässige Flächen¬ pressung ist vorteilhaft ein mit geringeren radialen Abmessungen einsetzbarer Reibbelag verwendbar, der folglich eine weniger Bauraum beanspruchende Gestaltung der gesamten Spannvorrichtung ermöglicht, wodurch sich ein bedeutender Kostenvorteil einstellt.According to the invention, a friction lining consisting of an organic material is provided. The asbestos-free material which is advantageously used has material properties whose maximum surface pressure reaches 2 N / mm 2 and thereby clearly exceeds the value of 0.5 N / m customary for plastics (eg elastomers or thermoplastics) . The coefficient of friction of the material according to the invention advantageously has temperature-dependent changes that are negligible compared to plastics. Due to the higher permissible surface pressure, a friction lining that can be used with smaller radial dimensions can advantageously be used, which consequently enables the entire clamping device to be designed in a smaller space, which results in a significant cost advantage.
Der konstruktive Aufbau der Spannvorrichtung sieht eine Aufteilung der Federkraft der einspannten Torsionsfeder vor, durch die in Umfangs- richtung eine Vorspannkraft auf den Riemen oder die Kette erzielt wird, und der zur Dämpfung eingesetzte Reibbelag ausschließlich von einer Axialkraft beaufschlagt wird. Unabhängig von der Stellung des Spannteils zum Basisteil stellt sich erfindungsgemäß keine Abhängig¬ keit zum Reibmoment ein, da das Reibelement und damit der Reibbelag von einer Axialkraft beaufschlagt wird, die konstant bleibt.The structural design of the tensioning device provides for a division of the spring force of the clamped torsion spring, by means of which a pretensioning force is achieved on the belt or chain in the circumferential direction, and the friction lining used for damping is only subjected to an axial force. Regardless of the position of the clamping part relative to the base part, there is no dependence on the frictional torque according to the invention, since the friction element and thus the friction lining is acted upon by an axial force which remains constant.
Vorteilhaft ist der Reibbelag auch keinerlei Verformungsarbeit ausge¬ setzt, die bei bisherigen Spannsystemen die Beibehaltung eines kon¬ stanten Reibkoeffizienten verhindert hat und damit die Lebensdauer des Reibbelages verringerte. Als ein geeigneter Werkstoff für den Reibbelag wird erfindungsgemäß ein astbestfreies Reibmaterial auf der Basis von Graphit-Duroplast- Kautschuk mit einer Kunstfaserarmierung eingesetzt, mit dem eine sehr hohe Verschleißfestigkeit erreichbar ist.The friction lining is advantageously also not subjected to any deformation work which has prevented the maintenance of a constant friction coefficient in previous clamping systems and thus reduced the life of the friction lining. According to the invention, a non-asbestos-free friction material based on graphite-duroplastic rubber with a synthetic fiber reinforcement, with which a very high wear resistance can be achieved, is used as a suitable material for the friction lining.
In einer konstruktiven Ausgestaltung liegt die Reibscheibe reibschlüs¬ sig an dem Reibbelag an, der am Basisteil befestigt ist. Alternativ kann der Reibbelag an der Reibscheibe befestigt sein und reibschlüssig am Basisteil anliegen. Die radiale Abmessung und Anordnung des Reib- belages ist vorteilhaft so gewählt, daß diese übereinstimmt mit der Kraftangriffsfläche der Feder, wobei der Reibbelag von der Feder durch den Boden des Basisteils getrennt ist. Der Erfindungsgedanke ist weiter übertragbar auf eine Reibbelaggestaltung, bei der der Reibbelag weder an der Reibscheibe noch am Basisteil befestigt, sondern als Los- teil eingesetzt ist. Vorteilhaft ist der Reibbelag in der geometri¬ schen Form einer Kreisringscheibe ausgebildet. Alternativ dazu bietet es sich ebenfalls an, den Reibbelag in Form axial oder radial geführ¬ ter Kreisringsegmente auszubilden.In a constructive embodiment, the friction disk rests frictionally on the friction lining, which is attached to the base part. Alternatively, the friction lining can be fastened to the friction disk and bear frictionally against the base part. The radial dimension and arrangement of the friction lining is advantageously chosen so that it coincides with the force application surface of the spring, the friction lining being separated from the spring by the base of the base part. The idea of the invention can also be transferred to a friction lining design in which the friction lining is neither attached to the friction disk nor to the base part, but is used as a loose part. The friction lining is advantageously designed in the geometrical form of an annular disk. Alternatively, it is also possible to design the friction lining in the form of axially or radially guided circular ring segments.
Zur Erreichung einer geschützten Anordnung des Reibbelages sieht der Erfindungsgedanke vor, daß die Außenwandung die Mantelfläche des Basisteils die Reibscheibe axial und radial überdeckt und damit eben¬ falls den Reibbelag einschließt. Diese Gestaltung ergibt gleichzeitig eine kompakte Bauweise, die einen geringen radialen und axialen Bau- räum beansprucht.To achieve a protected arrangement of the friction lining, the idea of the invention provides that the outer wall, the outer surface of the base part, covers the friction disk axially and radially and thus also includes the friction lining. At the same time, this design results in a compact design which takes up little radial and axial space.
Zur Schaffung einer reibungsarmen Lagerung für das Spannteil verbunden mit einer kompakten Bauweise soll gemäß der Erfindung die Welle des Spannteils im Basisteil wälzgelagert sein, wobei zur Wälzlagerung zumindest ein Nadelkranz eingesetzt ist, deren Wälzkörper unmittelbar zwischen dem Gehäuse (Basisteil) und der Welle (Spannteil) eingesetzt sind, die jeweils mit Laufbahnen für die Wälzkörper versehen sind.To create a low-friction bearing for the clamping part combined with a compact design, according to the invention, the shaft of the clamping part should be roller-mounted in the base part, with at least one needle collar being used for the roller bearing, the roller bodies of which are located directly between the housing (base part) and the shaft (clamping part). are used, which are each provided with raceways for the rolling elements.
Alternativ sieht der Gedanke weiter eine den radialen Bauraum für die Lagerung der Welle nochmals verkleinernde Gleitlagerung vor. Zur weiteren Erläuterung der Erfindung wird auf die Zeichnung mit der zugehörigen Figurenbeschreibung verwiesen, in der ein Ausführungsbei¬ spiel die Erfindung weiter verdeutlicht.Alternatively, the idea further provides for a plain bearing that further reduces the radial installation space for mounting the shaft. To further explain the invention, reference is made to the drawing with the associated description of the figures, in which an exemplary embodiment further clarifies the invention.
Der Aufbau des erfindungsgemäßen Spannsystems 1 wird durch eine Schnittdarstellung verdeutlicht. Danach ist das Spannsystem 1 mit einem Basisteil 2 versehen, das eine weitestgehend rotationssym¬ metrische Gestalt aufweist und das auf einer Mantelfläche 3 mit zwei radial gegenüberliegend angeordneten Laschen 4 zur Befestigung des Spannsystems 1 an einem nicht dargestellten Gehäuse, z. B. einem Kurbelgehäuse einer Brennkraftmaschine versehen ist. Zentrisch ist das Basisteil 2 mit einer von einem endseitig eines Bodens 5 ausgehenden Hülse 6 versehen, die sich bis über das gegenüberliegende Ende der Mantelfläche 3 axial erstreckt. Eine in die Hülse 6 eingesetzte Welle 7, die über Gleitlagerbuchsen 8 gelagert ist, stellt eine Drehver¬ bindung zwischen einem Spannteil 9 und einer Reibscheibe 10 her.The structure of the clamping system 1 according to the invention is illustrated by a sectional view. Thereafter, the clamping system 1 is provided with a base part 2, which has a largely rotationally symmetrical shape and which on a lateral surface 3 with two radially opposite tabs 4 for fastening the clamping system 1 to a housing, not shown, for. B. is provided a crankcase of an internal combustion engine. Centrally, the base part 2 is provided with a sleeve 6, which extends from an end of a base 5 and extends axially over the opposite end of the lateral surface 3. A shaft 7 inserted into the sleeve 6, which is supported by slide bearing bushes 8, establishes a rotary connection between a clamping part 9 and a friction disk 10.
Zur Erreichung einer drehfesten Verbindung ist das Spannteil 9 bzw. die Reibscheibe 10 drehfest, z. B. über eine Verzahnung 11 mit dem entsprechenden Bauteil verbunden, wobei das abgesetzte, mit der Ver¬ zahnung 11 versehene Ende der Welle 7 mit dem Spannteil 9 oder der Reibscheibe 10 zur Drehfixierung verstemmt ist. Im Hohlraum 12, der sich axial vom Basisteil 2 bis in das Spannteil 9 erstreckt, ist eine Feder 13, als Torsionsfeder angeordnet, die als Schraubenfeder aus- gebildet ist, und in der Betriebsstellung des Spannsystems 1 das Spannteil 9 stets in eine die Riemen- bzw. Kettenspannung erhöhende Stellung verschwenkt. Zur Drehfixierung der Feder 13 sind deren Enden am Boden 5 bzw. am Spannteil 9 über Haltebleche 19 gesichert. Außermittig ist das Spannteil 9 an seiner dem Basisteil 2 gegenüber- liegenden Stirnseite mit einem Gehäuseansatz 14 versehen, in die eine Paßbohrung 15 mit einer anschließenden Gewindebohrung 16 eingebracht ist. Diese Bohrungen 15 und 16 dienen zur Aufnahme und Befestigung einer nicht dargestellten mit einem Ketten- oder Riementrieb in Ver¬ bindung stehenden Spannrolle. Die am Spannteil 9 befestigte und mit dem Basisteil 2 zusammenwirkende Reibscheibe 10 liegt mit einer kreis¬ ringförmigen Scheibe 17 reibend am Reibbelag 18 an. Eine von der Feder 13 auf das Spannteil 9 ausgeübte Axialkraft wird über die Welle 7 auf die Reibscheibe 10 übertragen, die eine Kraft auf den Reibbelag 18 ausübt und damit eine gewollte Dämpfung der Bewegung des Spannteils 9 bewirkt, z. B. bei auftretenden Stoßbelastungen im Riemen- oder Kettentrieb. Dabei ist die Mantelfläche 3 des Basisteils 2 axial über den Boden 5 reichend verlängert, wodurch der Reibbelag 18 vom Basisteil 2 axial und radial überdeckt wird und durch Einbeziehung der Reibscheibe 10 nahezu vollständig geschützt angeordnet ist. To achieve a rotationally fixed connection, the clamping part 9 or the friction disc 10 is rotatably, for. B. connected via a toothing 11 to the corresponding component, the stepped end, provided with the toothing 11, of the shaft 7 being caulked with the clamping part 9 or the friction disk 10 for rotational fixing. In the cavity 12, which extends axially from the base part 2 to the tensioning part 9, a spring 13 is arranged as a torsion spring, which is designed as a helical spring, and in the operating position of the tensioning system 1 the tensioning part 9 is always in a belt or chain tension increasing position pivoted. To fix the spring 13 in rotation, its ends are secured to the base 5 or to the tensioning part 9 by means of retaining plates 19. Off-center, the clamping part 9 is provided on its end face opposite the base part 2 with a housing extension 14, into which a fitting bore 15 with a subsequent threaded bore 16 is made. These bores 15 and 16 serve to receive and fasten a tensioning roller which is not shown and which is connected to a chain or belt drive. The friction disk 10, which is fastened to the tensioning part 9 and cooperates with the base part 2, abuts the friction lining 18 with an annular disk 17. An axial force exerted by the spring 13 on the clamping part 9 is transmitted via the shaft 7 to the friction disk 10, which exerts a force on the friction lining 18 and thus causes an intentional damping of the movement of the clamping part 9, e.g. B. when shock loads occur in the belt or chain drive. The outer surface 3 of the base part 2 is extended axially over the base 5, as a result of which the friction lining 18 is covered axially and radially by the base part 2 and is arranged in an almost completely protected manner by including the friction disk 10.
BezugszahlenlisteLIST OF REFERENCE NUMBERS
Figure imgf000008_0001
Figure imgf000008_0001

Claims

Ansprüche Expectations
1. Reibungsgedämpftes Spannsystem für Riemen- oder Kettentriebe, ins¬ besondere eingesetzt in Brennkraftmaschinen, mit einem ortsfesten Basisteil (2), das eine Hülse (6) aufweist, über das ein schwenkbares Spannteil (9) geführt ist, wobei zwischen dem Basisteil (2) und dem Spannteil (9) eine beide Bauteile verspannende und zueinander ver¬ drehende Feder (13) eingesetzt ist und zur Dämpfung der Stellbewegun- gen des Spannteils (9) ein in Kraftrichtung der Feder (13) beauf¬ schlagtes Reibelement vorgesehen ist, wobei auf eine drehfest mit dem Spannteil (9) verbundene Reibscheibe (10) des Reibelementes aus- schließlich eine Axialkraft wirkt und die Reibscheibe (10) über einen Reibbelag (18) am Basisteil (2) anliegt, dadurch gekennzeichnet, daß der Reibbelag aus einem organischen Material hergestellt ist.1. Friction-damped tensioning system for belt or chain drives, in particular used in internal combustion engines, with a stationary base part (2) which has a sleeve (6) over which a pivotable tensioning part (9) is guided, the base part (2 ) and the tensioning part (9) a spring (13) tensioning both components and rotating relative to one another is used and a friction element which is acted upon in the direction of force of the spring (13) is provided to dampen the adjusting movements of the tensioning part (9), wherein only an axial force acts on a friction disk (10) of the friction element which is connected to the tensioning part (9) in a manner fixed against relative rotation, and the friction disk (10) rests on the base part (2) via a friction lining (18), characterized in that the friction lining consists of an organic Material is made.
2. Reibungsgedämpftes Spannsystem nach Anspruch 1, dadurch gekenn- zeichnet, daß ein asbestfreies Reibmaterial auf der Basis von Graphit- Duroplast-Kautschuk als Reibbelag (18) vorgesehen ist.2. Friction-damped clamping system according to claim 1, characterized in that an asbestos-free friction material on the basis of graphite-duroplastic rubber is provided as a friction lining (18).
3. Reibungsgedämpftes Spannsystem nach Anspruch 1, dadurch gekenn¬ zeichnet, daß der Reibbelag (18) die geometrische Form einer Kreis- ringscheibe besitzt.3. Friction-damped clamping system according to claim 1, characterized gekenn¬ characterized in that the friction lining (18) has the geometric shape of an annular disc.
4. Reibungsgedämpftes Spannsystem nach Anspruch 1, dadurch gekenn¬ zeichnet, daß eine Mantelfläche (3) des Basisteils (2) die Reibscheibe (10) axial und radial überdeckt.4. Friction damped clamping system according to claim 1, characterized gekenn¬ characterized in that a lateral surface (3) of the base part (2) covers the friction disc (10) axially and radially.
5. Reibungsdämpftes Spannsystem nach Anspruch 1, dadurch gekennzeich¬ net, daß die Welle (7) in der Hülse (6) über zumindest einen Nadel¬ kranz wälzgelagert ist. GE NDERTE ANSPRÜCHE5. Friction damped clamping system according to claim 1, characterized gekennzeich¬ net that the shaft (7) in the sleeve (6) is roller-mounted on at least one needle ring. CHANGED REQUIREMENTS
[beim Internationalen Büro am 28. Dezember 1993 (28.12.93) eingegangen, ursprüngliche Ansprüche 1 und 2 geändert; alle weiteren Ansprüche unverändert (1 Seite)][Received at the International Bureau on December 28, 1993 (December 28, 1993), original claims 1 and 2 amended; all other claims unchanged (1 page)]
1. Reibungsgedämpftes Spannsystem für Riemen- oder Kettentriebe, ins¬ besondere eingesetzt in Brennkraftmaschinen, mit einem ortsfesten Basisteil (2), das eine Hülse (6) aufweist, über das ein schwenkbares Spannteil (9) geführt ist, wobei zwischen dem Basisteil (2) und dem Spannteil (9) eine beide Bauteile verspannende und zueinander ver¬ drehende Feder (13) eingesetzt ist und zur Dämpfung der Stellbewegun¬ gen des Spannteils (9) ein in Kraftrichtung der Feder (13) beauf¬ schlagtes Reibelement vorgesehen ist, wobei auf eine drehfest mit dem Spannteil (9) verbundene Reibscheibe (10) des Reibelementes aus- schließlich eine Axialkraft wirkt und die Reibscheibe (10) über einen Reibbelag (18) am Basisteil (2) anliegt, dadurch gekennzeichnet, daß ein asbestfreies Reibmaterial auf der Basis von Graphit-Duroplast- Kautschuk mit einer Faserarmierung als Reibbelag (18) vorgesehen ist.1. Friction-damped tensioning system for belt or chain drives, in particular used in internal combustion engines, with a stationary base part (2) which has a sleeve (6) over which a pivotable tensioning part (9) is guided, the base part (2 ) and the tensioning part (9) a spring (13) tensioning both components and rotating relative to one another is used and a friction element which is acted upon in the direction of force of the spring (13) is provided to dampen the adjusting movements of the tensioning part (9), wherein only an axial force acts on a friction disc (10) of the friction element, which is connected to the tensioning part (9) in a manner fixed against relative rotation, and the friction disc (10) rests on the base part (2) via a friction lining (18), characterized in that an asbestos-free friction material on the The basis of graphite-duroplastic rubber with a fiber reinforcement is provided as a friction lining (18).
2. Reibungsgedämpftes Spannsystem nach Anspruch 1, dadurch gekenn¬ zeichnet, daß der Reibbelag (18) mit einer Flächenpressung in der Größenordnung von 2 N/mm2 beaufschlagt werden kann.2. Friction-damped clamping system according to claim 1, characterized gekenn¬ characterized in that the friction lining (18) with a surface pressure in the order of 2 N / mm 2 can be applied.
3. Reibungsgedämpftes Spannsystem nach Anspruch 1, dadurch gekenn- zeichnet, daß der Reibbelag (18) die geometrische Form einer Kreis¬ ringscheibe besitzt.3. Friction-damped clamping system according to claim 1, characterized in that the friction lining (18) has the geometric shape of a circular washer.
4. Reibungsgedämpftes Spannsystem nach Anspruch 1, dadurch gekenn¬ zeichnet, daß eine Mantelfläche (3) des Basisteils (2) die Reibscheibe (10) axial und radial überdeckt.4. Friction damped clamping system according to claim 1, characterized gekenn¬ characterized in that a lateral surface (3) of the base part (2) covers the friction disc (10) axially and radially.
5. Reibungsdämpftes Spannsystem nach Anspruch 1, dadurch gekennzeich¬ net, daß die Welle (7) in der Hülse (6) über zumindest einen Nadel¬ kranz wälzgelagert ist. 5. Friction damped clamping system according to claim 1, characterized gekennzeich¬ net that the shaft (7) in the sleeve (6) is roller-mounted on at least one needle ring.
PCT/EP1993/001809 1992-07-27 1993-07-10 Friction-damped tensioner for belt or chain drives WO1994002757A1 (en)

Priority Applications (3)

Application Number Priority Date Filing Date Title
JP50411194A JP3194954B2 (en) 1992-07-27 1993-07-10 Friction damping tensioning mechanism for belt or chain transmission
US08/356,329 US5458541A (en) 1992-07-27 1993-07-10 Friction-damper tensioning system for belt or chain drives
KR1019950700319A KR100260962B1 (en) 1992-07-27 1993-07-10 Friction-damped tensioner for belt of chain drives

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DEP4224759.4 1992-07-27
DE4224759A DE4224759C2 (en) 1992-07-27 1992-07-27 Tensioning system, friction damped for belt or chain drives

Publications (1)

Publication Number Publication Date
WO1994002757A1 true WO1994002757A1 (en) 1994-02-03

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US (1) US5458541A (en)
JP (1) JP3194954B2 (en)
KR (1) KR100260962B1 (en)
DE (1) DE4224759C2 (en)
WO (1) WO1994002757A1 (en)

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DE602005027001D1 (en) 2005-04-20 2011-04-28 Dayco Europe Srl IN THE PRESENCE OF OIL WORKING CLAMPING DEVICE FOR A BELT DRIVE
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US5458541A (en) 1995-10-17
DE4224759C2 (en) 2002-04-18
DE4224759A1 (en) 1994-02-03
KR950702686A (en) 1995-07-29
JP3194954B2 (en) 2001-08-06
JPH07509047A (en) 1995-10-05
KR100260962B1 (en) 2000-08-01

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